Reversible meter adjustment



OGL 22, 1957 E. THoREsEN REVERSIBLE METER ADJUSTMENT 2 Sheets-Sheet lFiled Deo. l0, 1951 llll llllll INVENTOR ElNAR THORESEN ATTORNEYS Oct22, 1957 E. THoRx-:SEN

REVERSIBLE METER ADJUSTMENT 2 Sheets-Sheet 2 Filed Dec. l0, 1951INVENTOR ATTORNEYS United States Patent O REVERSIBLE METER ADJUSTMENTEinar Thoresen, Pittsburgh, Pa., assigner to Rockwell ManufacturingCompany, Pittsburgh, Pa., a corporationV of PennsylvaniapplicationDecember`10, 1951,1Serial' No. 260,797` 9 Claims. (Cl. 74-394)The present invention relates to improvements in that type of couplingfor interconnecting'rotatable driving and driven members which isadjustable to modify the angular velocity ratio between sucht rotatabledriving andi driven members within predetermined limits. Morespecically, in its preferred' embodiment to be herein described, thepresent invention relates to improvementsA in the specific form of suchdrive couplings used in meters and known asaccuracy regulator mechanismswhich are interposed between the output of a measuring device and theinput of a registering device of a liquid meter or the like. Suchmechanisms provide al variable means for bringing the registration ofthe registeringy device into accord with the actual volumel of liquidpassed through the measuring device. The necessity for this compensationarises from several sources suchf as differences in physicalcharacteristics between diiferent liquids and variations in the physicalcharacteristics of a given liquid under different operating conditions.For example, such accuracy regulators are used to compensate fortemperature and viscosity variations.

The accuracy regulators disclosed in United States Letters Patent No.2,079,197, issued May 4, 1937, to C. P. Bergman, and No. 2,438,934,issued April 6, 1948, to W. H. Marsh are illustrative of prior artdevices over which my present invention constitutes an improvement.

In certain meter installations, it may be necessary for fluid to passthrough the measuring device of a meter in either forward or reversedirections. An example of such an installation is a meter for a storagetank into which the fluid is supplied andl from which fluid is withdrawnthrough a common line connection. For such meter installations, since itis usually desired tofaccurat'ely measure the ilow both into and out ofthe storage tank so that an accurate indication of the quantity offluid' retained in the tank is available, it is imperative that themeter be equally accurate in its flow registration for both directionsof fluid flow through the measuring device.

The accuracy regulators heretofore available such as those of theabove-identified patents, have not been capable of effecting suchaccuracy of registration for both directions of fluid ow through themeter, and this invention solves that problem.

It is, therefore, the primary object of my present invention to providean accuracy regulator for meters which is of such improved constructionthat the accuracy of the meter registrationv can be regulated for fluidflow in either direction throughthe measuring device of a meter.

It isv a further objecty of my inventionl to provide an improvedaccuracy regulator which is eifective to regulate the accuracy of owregistration for either direction ofA flow of fluid throughv themeasuring device of the meter and inV which the accuracy compensationfor both. directionsv of iiuid'` flow is effected by manipulationr of asingle adjustment.

More specifically it is an object ofl my invention to provide as anaccuracy regulatorA for.v meters a drive coup-ling for' interconnectingrotatable driving anddriven Patented Oct. 22, 19.57

ICS`

2' members which is'` adjustable within a predetermined range to effecta modification of the angular velocity ratio between such4 rotatablemembers which is common to both directions of rotation of such members.

Still more specifically, it is an objectof myV invention to provide asingle compact mechanism for this purpose which comprises basically airst gear rotatable with the driven member, a support rotatable'with thedriving merriber, a second gear rotatable with and relative' to thesupport in constant mesh with the rst gear, and a mechanism cyclicallyoperablein timedy relation with' the rotation of the support to impartrotation toY the second gear relative to thesupport whichv is of avariable amplitude and of a sense corresponding to the drivingmember'sense of rotation so that the angular velocity ratio between thedriving and driven members can bey modified within predetermined limitstof'effect equally accurate meter registration in both directions offluid ii'ow therethrough.

These and"v other objects of my invention will become apparent as thefollowing' detailed description proceeds in reference tothe-accompanyingdrawing wherein' like refer'- ence numerals have been used throughoutthe several views and wherein:

Figure lf is al side elevational view of the present preferred form ofaccuracy' regulator embodying the principles of my invention;

Figure 2 is avertical sectional view of such accuracy regulator takensubstantially along: the line 2--2 of Figurev l;

Figure 3 is a sectional plan view of such: accuracy regulator takensubstantiallyV along line 3 3 of Figure 2; and

Figure 4 is an enlarged fragmentary sectional' view of my accuracyregulator taken' substantially along the line 4 4 of Figure 3'.

Referring first to Figures 1 and 2 of the drawings, the accuracyregulator of my present invention is provided with aV housing supportstructurev formed of mating lower and upper housing parts 10 and 12-upon` which are journalled respectively a driving or input shaft'14 anda driven or output shaft 16. When this mechanism is coupled as anaccuracy regulator in a fluid meter, the input shaft 14 is driven by themeasuring device of such a meterand the output shaft 16 is coupled todrive the registering mechanism thereof. In the disclosed embodiment ofmy invention, shafts 14 and 16 are coaxially aligned.

A mechanism, generally designated 18, forms a positive drive connectionbetween shafts 14 and 16 to establish a predetermined angular velocityratio between shafts 14 and 16 which is` common to the two possibledirections of rotation of these shafts. In the disclosed embodiment, thepredetermined angular velocity ratio between shafts 14l and 16 is 1:1.The coupling mechanism 18, asv will appear presently, may be adjustedwithin fixed limits to modify this predetermined angular velocity ratiobetween the shafts 14 and 16.

The basic structure of the preferred embodiment' of my inventioncomprises a rst gear fixed for coaxial rotation with the output shaft16, a support iixed for coaxial rotation with the inputfshaft 14, asecond gear mounted on the support for rotation therewith and relativethereto in constant mesh with the iirst gear, and a mechanism operableirrespective of the direction of rotation of the shafts 14 and 16 tocyclically impart rotational movement of a controllable amplitude to thesecond gear relative to the support in timed relation to the supportrotation.

The said first gear is gear 19 which is suitably fixed near the lowerend of. shaft 16 below a bushing 20 by which shaft 16 is journalled uponupper housing part 12. The

upwardly projectingV hub of gear 19 extends into al recess 22 formedcoaxially in the adjacent face of bushing 20, the end face of thatvhubbeing'resiliently biasedinto abutment with*v the' end wall of recess22' to provide a slight 3 t drag upon the output shaft for a purposewhich will appear presently.

The resilient upward bias of gear19 and shaft 16 is produced by anelongated leaf or compression spring 26 which, at its ends, bears uponthe external surface of thc housing part 12, and is centrally aperturedat 27 to rotatably pass shaft 16 therethrough. In the illustratedposition of Figure 2. spring 26 is partially iiexed, a spring clip 28being fixed on shaft 16 to limit upward axial movement of the spring 26relative to the shaft 16 and to hold spring 26 under compression.

The said support fixed for rotation upon the input shaft 14 is acage-like structure` shown best in Figure 4 and formed of top and bottomplates 30 and 32 which are held in spaced parallel relation by parallelend members 34 and 36. Members 30, 32, 34 and 36 are suitably securedtogether, as by screws (notshown), to form a rigid cage-like supportstructure. The lower plate 32 is fixed for rotation with the input shaft14, input shaft 14 being formed with a radially extending flange 38 anda coaxially aligned upwardly projecting pin 40 to respectively supportand align the plate 32 relative to the shaft 14. The shaft 14 and plate32 are suitably secured together to form a unitary structure as bybrazing.

The upper plate 30 has a central cylindrical aperture 42 which `receivesa downwardly projecting cylindrical portion 43 of the bushing 20 toprovide an upper radial and thrust pilot bearing for the cage-likesupport. The lower end of shaft 16 is journalled below gear 19 in aspaced plate 45 rigid with upper support plate 30.

As is shown in Figure 4, the end members 34 and 36 support a throughshaft 44, the axis of which is normal to thesupport axis of rotation andupon which is axially slidably and rotatably mounted a worm 46.` As isshown in Figure 2, a pair of gear clusters 48 and 50 are journalledrespectively for rotation between the upper `and lower plates 30 and 32on opposite sides of the worm shaft 44 about axis spaced from andparallel to the common axis of shafts 14 and 16. The upper gear 49 ofgear cluster 50 is a worm wheel which is in constant meshing engagementwith the worm 46. The lower gears 51 and 53 of clusters 48 and 50 areconstantly meshed with each other. The upper gear 55 of cluster 48 is inconstant meshing engagement with the gear 19 on the output shaft 16.

From the structure thus far described, it is apparent that if the gearcluster 48 is held against rotation relative to the cage-like supportupon which it is journalled, rotation of the input shaft 14 will producerotation of the output shaft 16 at a like angular velocity, the supportand gears forming a rigid drive connection therebetween. It is furtherapparent that, if the gear cluster 48 is caused to rotate a given amountrelative to the cage-like support upon which it is journalled during therotation of the input shaft and the cage-like support, the angularvelocity of the output shaft 16 will be modified proportionately.Modification of the amount of rotation of gear cluster 48 during eachcycle of rotation of input shaft 14 will produce a correspondingmodification in the angular velocity ratio between shafts 14 and 16.`Rotation of gear cluster 48 relative to the cage-like support upon whichit is journalled is controlled through the direct drive connection fromgear cluster 50 by controlled rotary actuation of worm 46.

As shown in Figure 4, the opposite ends of worm 46 are formedrespectively with sets of ratcheted clutch teeth 52 and 54. At the leftend of worm 46, as viewed in Figure 4, a first worm driving member 56 ismounted for unidirectional coaxial rotation relative to worm shaft 44,while at the opposite end of worm 46, a second worm driving member 58 issimilarly mounted for unidirectional coaxial rotation relative to wormshaft 44 in a direction opposite that of member 56A Members 56 and 58are formed respectively with sets of clutch teeth 60 and 62 which arecomplementary to and adapted respectivelyto be driv 4 ingly engaged withclutch teeth sets 52 and 54 upon the worm 46.

As was previously pointed out, worm 46 is rotatably and axially slidablyreceived upon the shaft 44. Also, as has been previously pointed out,the spring 26 (Figure 2) biases the end of the hub of gear 19 intosurface contact with the end wall of the recess 22 of bushing 20 toproduce a slight drag upon the gear train formed by gear 19 and gearclusters 48 and 50. As a result of this slight drag, rotation of thecage-like support will produce an axial thrust upon worm 46 which, solong as the direction of rotation of the input shaft 14 remainsconstant, will urge the worm 46 into driving engagement with one of thedriving members S6 or 58. Upon reversal of the direction of rotation ofinput shaft 14, shaft 16 and gear 19 will bc temporarily restrainedagainst rotation by spring 26 thus causing a slight rotation of gearclusters 48 and 5G which in turn will cause the worm 46 to slide axiallyof shaft 44 to drivingly engage the other of Stich driving members.

Driving member 56 is fixed to a sleeve 64 which surrounds and isrotatable relative to shaft 44 and upon the exterior of which isreceived a pair of unidirectional clutches 66 and 68 in juxtapositionwith the driving member 56. The clutches 66 and 68 are of the springbiased ball type, each having a plurality of spring biased balls 70disposed around the periphery thereof. Clutches 66 and 68 are fixed tothe driving member 56 by spaced rivets, such as 72. Clutch 66 isreceived within a recess 74 in a retainer 76 which is xed within anaperture 77 through end member 34 of the support.

The tubular member 64 projects through an aperture in the end wall ofthe recess 74 and is provided exteriorly of `retainer 76 with a washer78 and cotter pin 80 to axially tix tubular member 64, driving member56, and clutches 66 and 68 relative to the retainer 76 and end member 34of the cage-like support. The balls 70 of the clutch 66 engage thecylindrical wall of recess 74 to prevent relative rotation between theclutch 66 and the retainer 76 in the direction opposite to thatindicated by the arrow 81 and to permit rotation of the clutch 66relative to the retainer 76 in the direction of the arrow 81 in theconventional manner of clutches of this type. Clutch 66 thus serves as adetent to prevent reverse rotation of the driving member 56. i

A collar 82 surrounds and operatively engages the balls 70 of clutch 68in a manner similar to that in which the balls 70 of clutch 66 engagethe recess 74 of retainer 76. Clutches 66 and 68 are operative in thesame direction so that, when collar 82 is rotated in the directionindicated by the arrow 81, a drive connection is established through theballs 70 between collar 82 and the clutch 68. During such rotation, theballs 70 of the clutch 66 are forced against their associated springs topermit rotation of the clutches 66 and 68 and the drive member 56relative to the retainer 76. When the collar 82 `is rotated in thedirection opposite to that indicated by the arrow 81, clutches 66 and 68and drive member 56 are held against rotation relative to the cagelikesupport by the engagement of the balls 70 of the clutch 66 with thecylindrical wall of the recess 74 of the retainer 76, rotation of thecollar 82 relative to the clutch, 68 being possible due to thecompression of the springs associated with the balls 70 thereof.

The worm driving member 58 is similarly provided with ball clutches 84and 86, a retainer 88, a sleeve 90, a washer 92, a Cotter pin 94, rivets95, and a collar 96. The structure and function of `these parts areidentical with the corresponding parts associated with worm drivingmember 56 with the exception that clutches 84 and 86 are operable in adirection opposite to that of clutches 66 and 68 so that worm drivemember 58 is rotatable only in the direction indicated by the arrow 97.

. In order, to impart rotary movement to the worm driving members 56 and58 in timed relation with the gemma-ee rotation" of input shaft 14;. I2have. provideda a linkage, nowy to"y be. described, which causestheTrcollars; 8-2' and 96 to oscillate` conjointly through` limited rotarypaths about the worm shaft axis once during; each cycle of rotation ofthe input shaft 14a Movement of. collars 82 and 96 in the direction of.arrow 81` duringone half of their oscillatory cycle will only drivewormtdriving memv ber 56, andv reverse movement of collars 82 and 96 inthe direction of arrow 97` will onlyl drive wornrdriving memberv 58. Theamplitude of oscillation of! collars 82 and 96 may be varied fromy zeroto a maximumV predetermined value which is, of course, dependent uponthe maximum amount of angular velocity ratio variation that isdesiredfor accuracy regulation: of theI type of meter with which the mechanismis to be used;

The linkage controlling the oscillation of collars 82 and 96 is bestshown in Figures 2 andy 3, thes illustrated configuration of thatmechanism corresponding to af zero amplitude of oscillationY of collars82' and- 96.y 'Ihis linkage includes a pair of like collars 100 and 102which are formed respectively with projecting ears 104 and 106 betweenwhichl is fixed a yoke 108' by screws 110. Collars 100 and 102 arevreceived upon reduced portions of collars 96 and 82 respectively as is`shownin Figure 4, and are fixed' thereto inany suitable manner. As isshown in Figures 2 and^3,.-a`pin;111-, upon thefend of which isrotatably mounted a cam follower slide block 112, is lixed centrally ofyoke 108,- theaxis of pin 111 extending normal to and intersectingtheaxis of shaft 44. Cam follower 112 operatively engages an annular camtrack forming groove 1-14 formed internally of a ring 116. Ring 116 ispivotally mounted above a diametral axis by pivot pins' 118 and 120-Whichare pivotally received within bushings 1-22v and 124 respectively.The bushings 122 and 124are so tixed in diametrically opposed aperturesthrough the cylindrical side wall of upper housing member 12y that thepivot axis of ring 116 intersects andl is normal; tothe common axis orrotation of shafts 14 and16.

In the illustratedposition of ring 116, theplanes of the parallel topand bottom walls- 1126-and1-28ofgroove 114 are normal to the axisofshafts 14 and 16 so that, as shaft 14 rotates, cam follower 112 andyoke 108 will rotate therewith but their pivotal movement about the axisof shaft 44 will be zero. Underthis condition worm 46 is held stationaryand locks gear cluster 48 against rotation on its axis. If, however,lring 116 is pivoted about its axis to a position in which the parallelplanes of the walls 126 and 128 of groove 114 are inclined relative tothe axis of shafts 14 and 16, during each cycle of rotation of shaft 14,follower 112 and yoke 108 will be depressed below their illustratedpositions for one half of such cycle and elevated aboveV that positionfor the other half of such4 cycle. n

Thus, inclination of ring 11'6 produces oscillation of yoke 108 and thecollars 82 and 96 to drive `the worm drive members 56 and 58 duringalternate halves of the cycle of rotationr of shaft 14. An increaseinthe inv clination of ring 116 will produce a corresponding increase inthe amplitude of movement of members 56 and 58.

With reference to Figures 3' and 4` it will be seen that if shaft 16 isdriven by shaft 14 in the direction of arrow 142 by the interlocking ofworm 46, worm gear 49, gears 53, 51 and gear 55 in engagement with gear19, an additional predetermined amount of forward movement in the samedirection (arrow 142) is imparted to shaft 16 by the upward movement(Figure 3) of slide block 112 in tilted track 114 of ring 116 and yoke108, causing a. turning movement to collar 96, clutches 84, 86 andmember 58 and causing worm 46 to turn in the direction of arrow 97. Theturning movement of worm 46 in direction of arrow 97 transmitted throughworm gear 49 and gears 53, 51 and 55 to gear 19 on shaft 16 will causeshaft 16 to turn an additional amount in the same direction (arrow 142).

When meter rotation is reversed, drive shaft 14V with the cage7 assemblywill turn in direction of arrow 144, and worml 46will slide'towardf theleftI (Figure 4) thereby disengaging. the right hand driving clutchassembly andfengaging clutch teeth 52 and 60'.l

Output shaft 16 will be driven by the interlocked gears as.- abovedescribed in direction of arrow 144 and will at the same time receive anadditional forward movement dueto the turning: of worm 46 in directionof arrow 81 (Figure-41).

This additional forward movement of shaft 16 in the direction of arrow144 i's imparted by the downward travel (Figure 3) ofslide block 112l intrack 114 of tilted ring 116 imparting a rotary motion to collar 82 inLdirection of arrow 81. This motion in tur-n is transmitted through:clutch 68, clutch teeth 60 and 52, worm 46, wormgear- 49 and. gearsh 53,51 and 55 to shaft 16 by gear 19.

It will thus be seen that a movement of worm 46 in direction of` arrow81 will cause output shaft 16 to turn an` additional amount for eachrevolution` of shaft 14 and in the same-*direction (arrow 144) In.-order to facilitate the adjustment of the inclination of ring.11!6,. Ihave provided an indicator plate 130, fixed to the upper housingV member12 by screws 132, and a coactingv indicator arm'v 134, which is suitablyfixed toa collar 136 which is in turn fixed upon an extension of pivotpin 120 of ring 116. As is shown in Figure l, plate 130, which isprovided with suitable indicia forming a` scale indicative of thepercentage of change of angular velocity `of output shaft 16, and anindicator arm- 134, which is providedwith a pointer 137, coact to form.a convenient indicating mechanism to facilitate adjustment of theangular velocity ratio between shafts. 14 and 16. A screw 138, whichextends through an elongated arcuate slot 140 in arm 134, is threadedlyengaged with plate so that by manipulation of screw 138,

armx 134- may befclamped to or released from plate 130 to respectivelylix or release ring 116.

From the foregoing detailed description it is apparent that IV haveprovided a simple and compact drive coupling for interposition between aregistering mechanism and a measuringf device ofameter which isadjustable to modify the angular velocity ratio between the input of theformer and the output of the latter to any value within the rangey ofthe adjustment for either direction of drive therebetween.

The invention may be embodied in other specilic forms without departingfrom the spirit or essential characteristics thereof. be considered inall respects as illustrative and not Iestrictive, the scope of theinvention being indicated by the appended claims rather than by theforegoing description, and all changes which come within the meaning andrange of equivalency' of the claims are therefore intended to beembraced therein.

What is claimed and desired to be secured by United States LettersPatent is:

l-. Incombination, support structure, an input shaft rotatable; ineither a forward or a reverse direction, an

output shaft similarly reversibly rotatable, a drive con'- nectioncomprising a system of gearing between said shafts establishing apredetermined angular velocity ratio therebetween common tor bothdirections of rotation thereof, two one way clutches, one or the otherof which is automatically engaged with said gearing depending upon thedirection of rotation of said input shaft, and means operable upon saiddrive connection to modify such common angular velocity ratio, saidlast-named means comprising a cam and follower connection between saidclutches and said support structure which,

when operative, is cyclically effective in timed relation to therotation of said input shaft to impart an ancillary movement to saidoutput shaft which is superimposed upon the normal movement impartedthereto from saisi The present embodiment is therefore to input shaftthrough said drive connection and which is common to both directions ofrotation of said input shaft.

2. In combination, an input shaft and an output shaft journalled forrotation about a common axis, a cage mounted on said input shaft forrotation therewith, a worm journalled on said cage for rotation about anaxis normal to said common axis, first and second worm drive membersdisposed respectively at the opposite ends of` said worm, meansmountingsaid first drive member for unidirectional rotation coaxiallywith said worm, means mounting said second drive member forunidirectional rotation coaxially with said worm in a direction oppositeto that of said first drive member, means cyclically operative in timedrelation with the rotation of said input shaft for alternately impartingsuch opposite unidirectional rotation to said drive members, meansadjustable to vary the amplitude of rotationalmovement imparted to saiddrive members between predetermined limits, means responsive to thedirection of rotation of the said input shaft for alternativelyestablishing a drive connection between said worm and one of said drivemembers, means including said worm and operative independently of therotation thereof drivingly interconnecting said input and output shaftsfor concomitant rotation at a predetermined angular velocity ratio, saidlast named means being perative in response to rotation of said worm tomodify such angular velocity ratio in accordance with the adjustment ofsaid drive member rotational movement varying means.

3. The combination defined in claim 2 wherein such angular velocityratio modification is effected by the superimposition upon the normalrotational movement of said output shaft of an ancillary movementresulting from rotation of said worm.

4. In combination in an adjustment for varying a continuous drive, arotatable input shaft, an output gear coaxial with said input shaft andoperably connected to an output shaft, a carrier rotatable with saidinput shaft, a first gear on the carrier, a constantly meshed gear trainon the carrier interconnecting said first gear with the output gear, asecond rotatable gear on the carrier constantly meshed with said lirstgear, a worm gear on the carrier rotatable with said second gear, anarbor normal to the input shaft axis, a worm constantly meshed with saidworm gear slidable longitudinally of `said arbor,`

worm driving members rotatable about said arbor at opposite sides ofsaid worm, cooperating sets of clutch teeth on opposite ends of saidworm and the adjacent ends of said worm driving members for oppositeunidirectional drive of said worm when one orthe other set of teeth isengaged, mechanism responsive to rotation of said carrier for cyclicallyrocking said worm driving members, means for adjusting the amplitude ofsuch rocking, unidirectional clutch means between said worm drivingmembers and said mechanism, and means responsive to the direction ofrotation of said input shaft for shifting said worm to engage one orltheother of said cooperating sets of clutch teeth whenever said input shaftis rotating, said rocking of said worm serving to impart incrementaldrive impulses to rotation of the output shaft from the input shaft.

5. In the combination defined in claim 4, said mechanism vcomprising arelatively fixed cam track, a follower for said track and linkageinterconnecting said follower and both said worm driving members.

6. `In combination in mechanism for varying the drive ratio betweenrelatively rotatable input and output shafts mounted on a support, acarrier fixed on the input shaft, a first gear fixed on the outputshaft, a second gear assembly rotatably mounted on the carrier inVconstant mesh with said first gear, a pair of unidirectional clutchjaws rotatably mounted on said carrier, a clutch collar constantlygeared to said second gear assembly slidable between positions of'meshwith one or the other of said clutch jaws in response to the directionof rotation of said input shaft,

r and cooperating means on the support and carrier for periodicallyrotating said clutch jaws during rotation of said carrier wherebysupplemental angular movement is supplied to said output shaft, andmeans for adjusting the amplitude of said movement between predeterminedlimits.

7. In the mechanism defined in claim 6, means for exerting a light dragon said output shaft for causing shift of the clutch collar in responseto a change in direction of rotation of said input shaft.

8. In the mechanism defined in claim 6, said periodic rotating meanscomprising a fork common to both clutch jaws and a cam track pivotallymounted on said support 'having a cam follower connection with saidfork, and said adjustingtmeans comprising means for adjusting and fixingthe pivotal position of said cam track.

9. In combination, stationary support structure, an input shaftrotatably mounted in said support structure for rotation in either aforward or a reverse direction, an output shaft rotatably mounted insaid support structure for rotation in either a forward or a reversedirection, a constantly engaged drive connection between said shafts, npair of opposed one way clutches, means responsive to rotation of saidinput shaft in a forward direction for automatically engaging one ofsaid clutches with said drive connection and responsive to rotation ofsaid input shaft in a reverse direction for automatically engaging theother of said clutches with said drive connection, and means responsiveto rotation of said input shaft in either direction for cyclicallydriving each of said clutches whereby sup plementary drive impulses areimparted to said drive connection through the engaged clutch during bothforward and reverse rotation of said input shaft.

References Cited in the file of this patent UNITED STATES PATENTS1,220,373 Stande Mar. 27, 1917 1,234,771 Kiewicz July 31, 1917 1,818,407Laille Aug. 11, 1931 2,070,752 Roes Feb. 16, 1937 2,111,547 Bergman Mar.22, 1938 2,364,915 Pressler Dec. 12, 1944 2,399,493 Luehrs Apr. 30, 19462,535,774 Armelin Dec. 26, 1950 FOREIGN PATENTS 526,599 France Oct. 1l,1921

